Pattern controlled milling machine



Dec. 26, 1950 J. Q. BUCKLES ETAL PATTERN cou'moum MILLING MACHINE 6 Sheets-Sheet 1 Filed Feb. 28, 1946 IN VEN TORS JOHN (P. flue/a E5 By GEaese /7- LEA/5K) H T'TOENEYS S .Ne

lllllllll II B Dec. 26, 1950 J. ucK Es ETAL 2,535,896

PATTERN CONTROLLED MILLING MACHINE Filed Feb. 28, 1946 6 Sheets-Sheet 3p IN VEN TQRS JOHN 7. BUG/(LES 660366 ,9. LEA/5K) BY wmrmeop Ive/a1:

MJKMvWWM Dec. 26, 1950 J. Q. BucKLEs EFAL 2,535,396

PATTERN CONTROLLED MILLING MACHINE Filed Feb. 28, 1946 6 Sheets-Sheet 4 INVENTORS M ZOE wow $34912? arrow/firs Dec. 26, 1950 l J. O. BUCKLES ETAL 2,535,896

PA'B'I'ERN'CONTROLLED MILLING MACHINE Filed Feb. 28, 1946 6 Sheets-Sheet 5 INVENFORS John Q.Buckles F E Gear A.Len.sk y

Wtrg Iu'op Trible.

BY )1. 21M m6. 7%

ATTORNEYS J. Q. BUCKLES. ET AL PATTERN CONTROLLED l lILLING l lACl-1INE 6 Sheets-Sheet 6 INVENTORS JOHN aue/ass 6504965 ll. lE/vsK) BY wmrmea Te/azE Filed Feb. 28, 1946 Patented Dec. 26, 1950 UNITED r rarrsau con'raonnan MILLING meme John Q. Buckles, George A. Leneky, and Winthrop Trihle, Cincinnati, Ohio, assignors to The Cincinnati Milling Machine 00., Cincinnati, Ohio, a corporation of Ohio Application February 28, 1948, No. 650,808

"1 18 Claims. This invention relates to machine tools and more particularly to automatic pattern controlled milling machines. I

One of the objects of this invention is to provide an improved machine for automatically progressively producing profile surfaces on the periphery of a rotatable workpiece from a pattern or master. I

Another object of this invention is to provide an improved automatic pattern controlled milling machine for machining simultaneously a series of non-contiguous profile surfaces on a plurality of continuously revolving work pieces in one continuous automatic cycle.

Still another object is toprovide an improved combined electric and hydraulic operating and control circuit for a rotary profile milling machine. 1

A further object of this invention is to provide a machine in which the cutter may be moved into engagement with a random point on the surface of a continuously rotating work piece but in which a predetermined angle of rotation of the work from said random point will be sub- 7 sequently effected, followed by separation between the cutter and work whereby the cutter may be rendered effective on the work for a full revolution, or more or less than a full revolution thereof regardless of the starting point of the cutter.

Other objects and advantages of the present invention should be readily apparent by reference to the following specification, considered in conjunction with the accompanying drawings forming a part thereof, and it is to be understood that any modifications may be made in the exact structural details there shown and described, within the scope of the appended claims, without departing from or exceeding the spirit of the invention.

Throughout the several views of the drawings similar reference characters are employed to denote the same or similar parts.

Figure 1 is a front elevational view of a multiple spindle pattern controlled milling machine incorporating the features of this invention.

Figure 215 a left hand end elevation of the machine shown in Figure 1.

Figure 3 is a vertical sectional view on the line '3--3 of Figure 1. t

the use 1-4 of clutch sum mammary the line l--l in n:- ure 6. w

Figure 9 is a sectionalview on the line 8-! of Figure 8.

Figure 10 is an enlarged diagrammatic view indicatedby the line lfl-il in Figure 1 showing the relationship of the cutter, work, tracer, and 1 pattern at the beginning of a cutting cycle on one of the peripheral profile surfaces on the work.

Figure 10a is a diagrammatic view similar to Figure 10 showing the relationship of the cutter. work, tracer, and pattern at the time of ini' tial engagement of the tracer with the pattern.

Figure 10bis a diagrammatic view similar-to Figure 10 showing the relationship of the cutter, work, tracer, and pattern at the completion of cutting the rofile surface on the work.

Figure 10%: is a diagrammatic view similar to Figure 10 showing the relationship of the cutter, work, tracer, and patternretracted to position for movementinto position to machine a" different profile surface on the work.

Figure 11 is a diagrammatic view similar to Figure 10 indicated by the line "-4 I in Figure 1 showing the relationship of the cutter, work, tracer, and pattern at the beginning of a. cutting cycle on a dififerent peripheral profile surface on the work.

Figure 11a is a diagrammatic view similar'to Figure 11 showing the relationship of the cutter, work, tracer, and pattern at the time of initial engagement of the tracer with the pattern.

Figure 11b is a diagrammatic view similar to Figure 11 showing the relationship of the cutter. work, tracer, and pattern at the completion of cutting the profile surface on the work.

Figure 110 is a diagrammatic view similar to Figure 11 showing the relationship of the cutter,

work, tracer, and pattern retracted to position for movement into position to machine still another profile surface on the work.

Figure 12 is an elementary wiring diagram of the electric control circuit of the machine.

Figure 13 is a diagram of the hydraulic operating circuit for the machine.

As an example of a machine adapted to carry out the concepts of this invention, there is illustrated a multiple spindle pattern controlled milling machine for machining slots in airplane cylinder heads to form the heat radiating fins thereon.

Work spindle drive Such a machine comprises a base 20 upon which are appropriately journaled a series of rotary work supports 2| and a pattern support 22. All of these supports are rotated synchonously through a common drive shaft 23, Figure 13, upon which is fixed a series of worms 24 which operatively engage identical worm wheels assaaaa 3 25 fixed to the supports 2| and 22. The shaft 23 is driven by the hydraulic feed motor 28 through suitable gearing 21 so that when this motor is actuated the supports are simultaneously and continuously rotated in accordance with the operation of the motor.

Cross slide On the rearwardly extending portion of the base 20 is formed guideways 28 upon which is slidably mounted cross slide 29 for movement to and from the work supports 2| and pattern support 22. This cross slide 29 is actuated in cross feeding movement in either direction by means of a hydraulic actuator or cylinder 30, Figure 2, which is rigidly fixed to the surface 3| of the base 2|! and has operating therein a piston 32 to which is attached the piston rod 33 connected to an integral lug 29a formed on the cross slide 29 so that by the application of fluid pressure in the cylinder 30 its piston 32 and thereby the cross slide 29 maybe reciprocated.

Spindle carrier n appropriate vertically disposed guideways 34 formed on the front face of the cross slide 29 is mounted for vertical movement the spindle carrier 35 which may be reciprocated vertically by means of a hydraulic cylinder '35, Figure 13, suitably fixed to the cross slide housing 29 and having a piston 31 and an associated piston rod 38 suitably attached to the spindle carrier 35 so that upon appropriate application of fluid pressure in the cylinder 36 the spindle carrier may be raised or lowered on the guideways 34.

The spindle carrier 35 comprises a horizontally elongated housing upon which is fixed a series of tool or cutter spindle brackets 39 in which are journaled the cutter spindles 40. Each of these cutter spindles carries a cutter arbor 4| upon which is mounted the milling cutters 42. Each pair of cutter spindles is driven by one of the cutter motors 43 connected through their respective pulleys 44 and belts 45 to pulleys 48 carried by the cutter spindles 40 so that the cutter spindles and cutters may be rotated at cutting speed for any vertical position of the spindle carrier.

Also mounted on the spindle carrier 35 is the tracer support bracket 41 carrying the tracer valve 48 having a pattern contacting tracer disc 49 which is the same diameter as the cutters 42 being utilized to machine the work. This tracer disc is arranged to engage the pattern array P mounted rigidly on the pattern support 22, Figure 1.

General operating cycle In this particular exemplary disclosure the workpiece comprises an airplane cylinder head W having a main cylindrical portion upon which the heat radiating fins F are formed by milling away the metal to form the slots S, Figures b, 10c, 11b, and lie, in planes perpendicular to the axis 50 of the work support and the cylinder barrel cavity 51 of the cylinder head. Suitable clamping fixtures or chucks C serve to locate and hold the work W on the work supports 2| in proper relationship with the cutters 42 and the pattern array P.

The slots to be out are spaced axially of the work and may vary greatly as to depth and configuration. For instance, in this specific workpiece the metal to be cut away to form one of the slots is indicated in Figures 101) and 100 by the uncross-hatched portion 52. The depth and configuration of the bottom 53 of the slot 52 is determined by its related template 52a of the pattern array P. This template cooperates with the tracer disc of the tracer control valve 48 as the template and work continuously rotate during the cutting operation to control the relative radial movement of tracer and cutter with respect to the pattern array P and work W.

In Figure 10 is shown the relative position of the cutter and tracer with respect to the work and pattern at the beginning of a cutting cycle with the cutter and tracer in fully retracted position. To begin the machining operation the work and pattern are started and continuously rotated at all times during the machining of the slots in the work pieces. with the work and pattern thus rotating continuously the cutter and tracer are respectively fed radially of the work and pattern along the lines 54 and 55 so that the cutter initially engages the workpiece at some random point 56, Figure 10a. It is therefore obvious that initial contact of the cutter and workpiece may occur at any random point on the periphery of "the work.

As the work slowly rotates and the cutters continue to feed radially toward the work an involute path 51 is initially cut into the workpiece until the cutter reaches full depth of the desired slot at a point 59 as determined by engagement of the tracer disc 49 with the pattern 52a at. a point 59 to thereby establish tracer control movement of the cutters radially of the work pieces. At this point the workpieces are preferably rotated at a more rapid feed rate to cause the cutter to relatively travel around the periphery of the work to machine the slot 52, as shown in Figure 10b, the cutter ultimately arriving at the point 60 on the work and the tracer disc at the point 68a on the pattern 52a. It is desirable that the work supports and pattern rotate through slightly more than 360 degrees regardless of the starting point, as indicated by the angle Si in order to provide a sufiicient overlap of the cut from initial starting position to completely machine the slot 52 without leaving an undesirable flash or unmachined portion in the slot. When the point 60 is reached the cutter and tracer are rapidly withdrawn radially along the lines 54 and 55, Figure 10c, while the work and pattern continue to rotate at a predetermined slow speed.

When the cutter and tracer have arrived at the withdrawn position shown in Figure the cutter and tracer are then indexed upwardly into position to out another slot as, for example, a slot of the character shown in Figure 11. The

work and pattern continue to rotate at all times so that as the cutter and tracer again move radially inwardly along the lines 54 and 55, Figure 11, the cutter will begin to engage the work at some random point 62, Figure 11a, and will cut a spiral inwardly extending slot 63 in the work until the cutter arrives at the point 64 at which time the tracer disc 49 engages the corresponding pattern 65a at a point 84a to stop the feed and subsequently control the proper form for the slot 65 to be machined in the work. Tracer control is thus established and the work continues to rotate through a complete revolution of 360 degrees plus a small additional amount indicated by the angle 65, Figure 11b, until the cutter arrives at the point 61. The cutter and tracer are then automatically retracted along the lines 54 and 55 as indicated in Figure to a withdrawn position where the cutter and tracer may again be moved or indexed into position to 5 p I cut still other slots. After the last slot is cut the cutter and tracer are returned downwardly to initial starting position preparatory to cutting a group of slots on a new set of workpieces.

It is to be noted that the configuration of each individual slot may be quite irregular as shown in Figure 188 and that there is considerable variation from one slot to another as indicated by a comparison of Figures 1012 and 11b. In order to maintain the highest degree of cutting efliciency, it is necessary to vary the rate of rotation or feed movement of the work spindles in accordance with rapid changes in profile. ,As a result the time required for the work to rotate a complete revolution and a small amount in excess thereof is subject to considerable difference from one slot to the next. In order to accurately determine the point of withdrawal of the cutter from the work, as in Figures 108 and 11b, without requiring the work to rotate an excessive amount beyond that necessary to just complete a slot, a mechanical angular rotation measuring device directly responsive to the amount of rotation of the work and independent of the time required for such rotation is provided.

Hydraulic operating system The work spindles, cross slide, and spindle carrier are operated in their various movements to carry out the above-described machining cycle by hydraulic pressure actuating mechanism. Referring particularly toFigure l3, fluid pressure for operating the machine is derived from a pump 66 which receives a supply of fluid from a hydraulic reservoir 81 through a suction line 68. This fluid is delivered under pressure into the line 88 having a branch line 68a connected to a suitable relief valve I8 which, in turn, is con nected by a drain line II to the reservoir 61. the relief valve serving to maintain the desired operating pressure in the line 68 and its associated branch lines.

The work supports II and pattern support 22 are started in rotary motion by energizing solenoid I2 which is connected through suitable linkage 18 to the plunger 14 of the stop and start pilot control valve I5 so as to connect pressure from the line 88 and the line 88b through the annular groove I8 of the plunger I4 to a line 'I'I connected to chamber I8 in the stop and start valve I8 so as to move its plunger 88 to the position shown in Figure 13. Fluid is exhausted at this time from chamber 8| through line 82 and the annular groove 83 in the valve plunger I4 to the drain line 88 for return to the reservoir 51. When the plunger 88 of the valve I8 is so positioned, fluid pressure from the line 68 and the branch lines 680 and 88d is connected through line 68c to a fluid resistance 85 which allows a,

pressure will be connected from the line 68b through the annular groove 88 and the line 82 to the chamber 8| of the valve I8 to thus shift its plunger 88, to the left, Figure 13, so as to block III Ill

by an additional supply from the line 58d and the line 88/ which is connected to a port 8| in the tracer valve 48. This port cooperates with an annular groove 82 formed inthe tracer valve plunger 88. The line 81 Is connected by means of a line 84 to the port 85a provided In the tracer H valve 48, port 8511 also cooperating with the an: nular groove 82 in the tracer valve plunger 88. The annular groove 82 is so arranged with, relation to the ports 8| and 85a that when thetracer valve plunger 83 is in normal tracing position with the tracer disc 48 in contact with the pat! tern, the supply of fluid pressure may pass from line 68) to line 94 and then to the hydraulic motor I 28 as described to rotate the work and pattern, I

supports at a normal rapid cutting feed rate. Whenever the tracer is deflected a markedamount from normal tracing position, as when the tracer is passing over an obstruction or illx to a cavity causing relatively rapid radialmova ment of the cutter with respect to 8116:;WOIk, the ports 8| and 85a will be controlled, so as to re strict the flow between lines 68 and 98; and thereby slow up the speed of rotation Inthis way, the rate of feed rotation of theworkand; pattern supports is automatically varied in ac f cordance with the rapidity of changes in the I profile of the pattern.

The tracer plunger 88 may be purposely over-g deflected in order to cause the cross slide to move back away from the work and to stay 1 in 1'91" tracted position by energizing solenoid 95 which is connected through suitable-linkage 8B for, moving the plunger 8'! of the cross slide contrclvalve 88 to connect pressure from the line 689 through: theannular groove 88 01' the valve plunger 81 to the line I88 connected toapressureplunger I8I which. through a suitable lever I I82, actuates;

the tracer plunger to overdeflected position.

When in overdeflected position the tracer valve; connects fluid pressure from the line 58h through the annular groove, I88 and the line I I88 to the chamber I85 of the cross slide actuating, cylinder 88, while fluid is discharged out of the, chamber I86 of the cylinder 88 through the line, I81 and the annular groove I88 inptheutracer, valve plunger 83 to the drain line I88 for return;

to the reservoir 51. I

When the tracer is released andmoved to unwdeflected position by the spring III, pressure, from the line 582' will be connected through the annular groove I88 to the line I8I,,then;to the. chamber I88 in the cross slide cylinder; 88 to cause forward movement of the crossslide 28, while fluid is discharged from theother chame 5 her I85 of the cylinder 88 through the line 184 and annular groove I88 of the tracer valveinto thedrainline I88. When the solenoid II8 is energized, the valve plunger 81 is po'sitionedas shown in Figure 13 so as to relieve pressure from: behind the plunger IN by connecting the line: I88 through the annular groove 88 of the plungers 8Ito the drainline I88, thus releasing the tracer plunger 88 to undefiected position. =Whenthe1 plunger 83 is operating in normal tracing position. the annular grooves I03 and I08 formed in the plunger cooperate withthe pressure lines 5812. and 58: and the drain line I03 to reversibly apply fluid pressure to the cross slide operating cylinder 30 to actuate the cross slide 28 in tracer controlled movement in response to the configuration of the pattern.

Vertical indexing movement of the spindle carrier 35 for successively moving cutters and tracer into position to machine each slot on the workpiece is obtained by energizing the solenoid II2 which connects fluid pressure from the line 59 through the annular groove II3 of the plunger II4 of the indexing control valve II5 to the line H8. The line H8 is connected to the chamber H1 of the detent plunger cylinder II8, Figure 13, v

to cause withdrawal of the detent plunger H8 from the detent wheel I fixed on the shaft I2I of the index control assembly journaled in suitable bearings I22 and I23 of the spindle carrier 35. The detent plunger is thus withdrawn against a compression spring I24 in the chamber I25 of cylinder II8, fluid being discharged from this chamber through a line I28, annular groove I21 of the valve plunger I28 where it enters the drain line 84 for return to reservoir 51.

As the detent plunger II8 becomes fully withdrawn it connects pressure from the line II8 to the pressure chamber I3I to effect operation of the ratchet plunger I32. This plunger has a pawl I33, Figure 4, adapted to successively engage the various indexing notches I34 in the ratchet wheel I35 fixed on the shaft I2I. As pressure builds up in the chamber I3I the ratchet plunger I32 causes the pawl I33 to rotate the disc I35 and the shaft I2I one indexed position. I

As the plunger I32 reaches its forward position,

it shifts a control valve plunger I28, Figure 13,

so that fluid pressure is connected from the line 581 to the line I28 and thereby to the pressure chamber I24 to move the detent plunger II8 back into engagement with the detent disc I20.

As soon as the indexing has been completed the solenoid H2 is deenergized to disconnect line 68 from the line IIG while connecting line II8 through the annular groove II3 to the drain line 84. Thus, the chamber H1 in cylinder H8 is connected to drain line 84 so that the plunger H8 is free to move into engagement with the detent disc I20. At the same time the compression spring I35 behind the plunger I28 automatically returns the ratchet plunger I32 whereby pawl I33 drops into the next successive notch I34 of the ratchet disc I35. Fluid is discharged from the pressure chamber I3I behind the ratchet plunger I32 out through the line I30 and check valve I30a to the chamber H1 in the line II8 through the annular groove N3 of the valve II 5 to the drain line 84. Thus, whenever the solenoid H2 is energized, the shaft I2I of the indexing mechanism is indexed one notch, and when the solenoid H2 is deenergized the apparatus is then reset for the next indexing operation.

The indexing movement of piston 31 is controlled by means of a servo-valve I31 rigidly mounted onthe cross slide 23. This valve has an axially movable plunger I38 adapted to engage the steps I38 formed on the indexible drum I40 journaled in a suitable bearing I mounted on the spindle carrier 35. This drum is adapted to be driven through a suitable gearing indicated at G which may comprise a bevel gear I42 fixed to rotate with the drum I40 and driven by a second bevel gear I43 on a suitable shaft I44 carried in a suitable bearing I45 mounted on the spindle carrier 35. This shaft may be driven by a universal joint I45 and a drive shaft I41 and a universal joint I48 appropriately connected to drive the indexing shaft I2I as best seen in Figure 1. The drive is so arranged that with the indexing movement of the shaft I2I by the ratchet I35 the next successive step of the indexing drum I48 will be presented under the servo-valve plunger I38.

At the beginning of each machining cycle the drum will be rotated so as to each time drop the plunger I38 to the next succeeding lower step until the final bottom step I38b is reached. With the servo-valve plunger I38 on the step I38a, for instance. indexing of the drum I48 one notch will momentarily cause the servo-valve plunger to drop. This will cause pressure from the line 89k to be connected through the annular groove I48 to the line I50 which is connected to the lower chamber I5I of the cylinder 35 to thus cause the spindle carrier 35 to be raised, and this motion will-continue until the next step on the drum moves the valve to its neutral position to cut off fiow from the pressure line 587: to the line I50. Fluid is discharged from the chamber I52 of the cylinder 38 through the line I53, the annular groove I54 of valve plunger I38 into the drain line 84 for return of fiuid to the reservoir 81. Thus, as the shaft I2I is indexed by appropriately energizing the solenoid III of the indexing valve II5, the servo-valve will be momentarily unbalanced until the spindle carrier 35 has moved up to the next desired indexed position. this process continuing until all the indexed spaces on the drum I40 have been passed over and the valve plunger I38 of the servo-valve finally arrives at the last step I38b.

As the last indexed position I38b is reached, a cam I55 fixed on the shaft I2I becomes effective to actuate the plunger I58 of an index return control valve. This valve connects pressure from the line 88m through the annular groove I51 of the plunger I58 to the line I58 which is connected to a pressure plunger I58 which through a suitable leverage arrangement I lifts the servo-valve plunger I38 upwardly, Figure 13. This reverses the connection occurring during the normal step by step indexing to now connect pressure from the line 88k through the annular groove I54 of the plunger I38 to the line I53 and chamber I 52 of the cylinder 38 to rapidly move the cutter spindle carrier downwardly. Fluid is being discharged at this time from the cylinder chamber I5I through line I50 and groove I43 to the drain line 84. Thus, after the final indexing movement for the last slot, a final indexing of the shaft I2I causes the cam I55 to operate the valve plunger I58 to effect downward movement of the cutter spindle carrier 35 to its lowest positirlm, preparatory to beginning the next cutting cyc e.

The angular rotation measuring device previously referred to is provided in connection with the rotation of the work and pattern supports to automatically determine a prescribed angle of rotation of the work and pattern measured from the random point that the cutters have been fed to full working depth so that it is not necessary to have the work and pattern supports in any predetermined angular position when the cutter engages the work. This saves time and avoids the necessity for starting and stopping the work for-each slot. This mechanism auto- 9 matically begins functioning when the tracer has iully engaged the pattern and continues to tunetion until an exact amount 01 rotation of the work and pattern spindles has been eflected, in this particular case a full revolution plus small predetermined amount of angular rotation over the 360 degrees. This device operates independently oi any fluctuation in the overall time required for the work to rotate through the 360.

degree plus caused by the tracer varying the feed rate for different configurations o! the profile of the pattern. Furthermore, thisarrangement is independent of the starting point at which the cutters reach full depth of cut and depending shaft portion 22a of the pattern support 22 so that rotation 01' the pattern support positively drives the clutch spindle I66 in timed relationship with it.

Pressure supply from the line 66 through the branch line 661:, Figure 13, is connected to the timer control valve I66 having a plunger I66 actuated by the solenoid I16, so that when the solenoid I16 is energized the plunger will be moved so as to connect fluid pressure from the line 6611 through the annular groove I1I to the line I12 which is connected to a port I16 formed in the bracket I6I. This port communicates with an annular groove I16 formed in the periphery of the bushing I62. Radiallyextending passageways I16 in the bushing I62 communicate with an annular groove I16 formed in the clutch spindle I66. Thus, fluid pressure in line I12 is at all times connected to the annular grooves I16 and I16 for any rotative position oi the bushing I62 and clutch spindle I66. In the groove I16 of clutch spindle I66 is formed a series of radial passageways I11 which communicate with an axial passageway I16 extending downwardly to a radial passageway I16, this latter communicating directly with a pressure pocket I66 formed in one side of the bushing I62 having faces I6I, Figure 9, so that when fluid pressure enters the line I12 pressure will build up in the pressure pocket I66 to force the clutch spindle laterally and cause it to bind in the bore I66 of thebushing I62 andthus act as a clutch to connect the spindle I66 and bushing I62 for joint rotation. when fluid pressure is released from the line I12 by deenergizing solenoid I16 pressure will be released in thepressure pocket I66 and thereby disconnect clutch spindle I65 relative to the bushing I62. I I

In order to facilitate lateral displacement of the clutch spindle I66 when fluid pressure is applied in the pressure pocket I86 there is provided in the spindle I65 and opposite tothe pressure pocket a series of drainage grooves I62 extending longitudinally ofthe shaft I65 and communicating with an annular drainage groove I63 formed in the periphery of the spindle I65 so that as the shaft is displaced laterally the normal lubricating film existing between the spindle I66 and the bore I66 may readily escape into the grooves I62 and then into the drain groove I66 i to thus allow the spindle I" to be forced into metal to metal contact with the bore I66. Fluid from the annular groove I66 is drained of! through a series of radial passageways I66 to the annular groove I66 formed in the outer diameter of the bushing I62 which is connected to the drainpline I66.

In the bracket I6I is slidably mounted a rack bar I66 on which is formed teeth I61 which op- .eratively engage a pinion I66 formed on the lower end of the bushing I62 so that rotation of the bushing I62 will move the bar I66 axially in the bracket III. The bar or plunger I66 is normally urged to a position I6Ia. Figure 5, by compression spring I66 carried in a bore I66 formed in bracket I6I and abutting against a closure bushing I6I and against the flange I62 oi the plunger I66, the flange I62 in turn abutting against the end surface I66 of the bore I66 to limit the plungerin of the amount of angular rotation.

the position I6Ia. Plunger I66 has a stem I66a which engages a plunger I 66 axially slidable in the bushing I6I and which has an adjustable abutment screw I66 adapted to engage a roller I66 of a lever arm I61 of a control limit switch I66 mounted on the base 26 of the machine by suitable screws I66.

Normally when fluid pressure is released In'the line I12 by deenergizing the solenoid I16. the compression spring I66 acting against the plunger I66 holds the plunger in the position I6Ia and the spindle I66 is free to rotate in the bushing I62. The instant, however, that fluid pressure is applied in the line I12, the bushing I62, and thereiore its integral gear I66, are connected in ro- 35 tative engagement with the clutch spindle I 66 and the pattern support 22. Rotation of the pattern support rotates the gear I66 and moves the plunger I66, to the left, Figure 5, by, compressing the spring I66 to the position I6Ib,fat which time the end I66a or the plunger I66 operates the limit switch I66 through the plunger I66 as described. The ratio or the gearing provided by the gear I66 and the rack I61 is so arranged as to allow the pattern support and related work supports to rotate slightly mor than 360 degrees from the time fluid pressureis initially applied in the line I12 until the plunger, I66 actuates thecontrol limit switch I66. As soon, however, as pressure is released from the line I12, the plunger .166 immediately returns under the influence of the spring I69 to its original position16la. Thus,

in this way there is provided an accurate measuring device coordinatedwith the rotation of the pattern and work supports, such that at a given point the mechanism may be engaged to begin the movement of th rack plunger I66 and then after the work support has made a predetermined amount of rotation, in this instance slightly more than 360 degrees, a second control limit switch may be actuated. It is to be noted that the rate of rotation of the work support as it varies from one slot to another has no eitecton the accuracy Electrical control means To start the machine, the operator throws the lever 12a to start the work rotating and presses start button 200, which completes a circuit from line 20 I through closed contacts 2 I2a or an index interlock switch 2I2, to start relay 200a. Operation oi! this relay closes contacts 200D which establishes a'holding circuit 434 through stop button 000 around the starting switch.

Operation of relay 200a also closes contacts 2000 to complete a circuit from line 20I, through closed contacts 2I2a, start switch 200, and line 200 to solenoid relay I Ia. This efiects hydraulic release of the tracer plunger so that the cross slide moves forward to engage the cutters and tracer with the work and pattern respectively along the lines 00 and 00 in Figure 10. At this time, the work and pattern supports are continuously rotating, having been started by moving the lever 12a of the start and stop switches 12b and 90b in run position as shown in Figure 12, completing a circuit from 20I, switch 12b, lead 120, solenoid 12 to lead 204 to energize solenoid l2 and thus interconnect line 01 with line 00. Line 01 is supplied at this time from pressure line 09 through the hydraulic resistance 00.

The advancing motion of the cross slide continues until the cutters have reached their full depth and the tracer disk 49 has engaged the portion 02a of the pattern to establish tracer control of the cross slide. At this point the tracer is deflected a suilicient amount to cause actuation of the limit switch 201 mounted in axial alignment with the tracer valve plunger 00. The closing of switch 201 completes a circuit through a pair of normally closed switches 00b and 2I'Ia to control relay "M for solenoid I10. Operation of control relay I'I0a, closes relay contacts I'I0b which short circuits out switch 201 so that further deflection of the tracer will not disturb "0a.

The energization of solenoid I10 eflects hydraulic coupling of the clutch spindle I00 for actuation of the angular measuring device. After the work supports have completed slightly more than 360 degrees of rotation to finish machining of a slot 02, for example, as shown in Figure 10b at the point 00, the limit switch I00, Figure 5, is actuated by the plunger I00 completing a circuit from lead 20I, closed contacts I'l0c which were closed by operation of solenoid relay H011. to relay 00a. Operation of relay 00a causes operation of solenoid 00 which effects retraction of the tracer valve and withdrawal of the cross slide 20 to the retracted position shown in Figure 100.

It will be noted that operation of relay 05a opened normally closed contacts 90b in circuit of solenoid relay I'I0a whereby solenoid I is released to effect disengagement oi the hydraulic clutch whereby the rack plunger I80 is free to return under the impetus of spring I89.

Attention is invited to the fact that when switch 201 was closed by engagement of the tracer with the pattern, it opened the normally closed pair of contacts 201a associated with the switch, thereby breaking the circuit to relay I I0a. Release oi! this relay, permitted contacts I MD to close since these are normally closed contacts and now the operation of relay 00a closes contacts 900, thereby establishing a holding circuit around switch contacts II0c and I00. Thus the release of solenoid H011 and resultant opening of contacts l'l0c does not prevent the return or the cross slide.

As the cross slide reaches a retracted position of the cutter and tracer as shown in Figure 100, a limit switch 2 I0, mounted on the base 20 as shown in Figure 2 is actuated by a dog 2 to complete a circuit mm the lead an, limit switch in, lead 2IIa, normally closed contacts IIOc of released relay IIOa, to solenoid II2 to eflect upward indexing or the carrier 00 into position for cutting the next slot in the work as shown in Figure 11.

As the drum I00 indexes, the servo-valve plung er I00 and a rod Illa, which passes freely through a central bore in the plunger, both drop down due to withdrawal oi the step upon which they were both resting. The dropping 01' rod Illa, released limit switch 2I2, whereby contacts 2I2a and 2I2b assume the position shown in Figure 12. Contacts 2I2b are free to close because they are normally closed contacts and thus cause operacontacts 2I2a, closed contacts 2I0a, normally closed contacts 2I0a, closed contacts 2IIb, and closed contacts 2000 to solenoid relay I Ilia whereby solenoid IIO operates to start a new cycle of advance of the cross slide.

This operation of solenoid IIO immediately releases switch 201 so that its contacts 2010 close and establish a holding circuit to relay lIla which is maintained until the tracer engages the pattern, because as soon as the cross slide advances, the contacts 2 I lb will open due to release oi limit switch 220, and also the timer relay contacts 2I0a will open about this time.

The actuation oi relay 2II by limit switch 220 effected by the returning cross slide momentarily opened the normally closed contacts 2I'Ia associated therewith, thus breaking the circuit to relay I and opening its holding circuit contacts II0b so that this circuit is now reconditioned so that upon engagement of the tracer with the pattern, the switch 201 may be closed to again cause actuation oi the hydraulic clutch and measuring device.

This mode of operation continues until the last slot is cut whereupon a final indexing of the shaft I2I takes place without relative movement of the servo-valve. At this time, however, the plunger I00 of a control valve is operated by a cam I00 on the index shaft I2I to connect pressure to the line I08 to eflect upward shifting of the servovalve and downward return of the spindle carrier 00 to initial starting position.

As the spindle carrier 00 moves down to its initial starting position, a limit switch 2I0 carried by the spindle carrier engages a dog 2I0 on the cross slide and is operated to close a circuit from line 20I, switch 2I0, line 2I Ia and normally closed contacts 00 to solenoid II2, to effect a second indexing operation to bring the step I00a under the servo-valve plunger I00. This indexing movement of the shaft I2I causes the cam I00 to release the valve plunger I06 and thus release the servo-valve plunger which now drops down on step "0a.

Also, this final indexing movement of shaft I2I rotates the cam 2 to actuate the limit switch 2I0 to complete a circuit from line 20I to relay 2l0 which opens normally closed contacts 2I0a essence i3 to preventoperation oi solenoid Ill whereby the machine stops. i

The work may now be changed, and it is necessary to manually actuate the starting button 205 tostart a new cycle of operation.

, There has thus been provided an improved automatic profiling machine which will profile milla pluralityoi slots successively in a continuously rotating workpiece, and in spite of the fact that the cutter will engage the work at a random or unpredictable point around the periphery of the work. the machine is so contrived that such pointfis detected and the angular rotation of the work measured from that point so that the cutter is in engagement with the work for the same number of angular degrees for each slot cut regardless of the point of engagement with the work or the irregularity of the profile being out.

What is claimed is: o o 1. In a pattern controlled machine tool, the combination with continuously rotating supporting means for a work piece and a pattern, of a cutter and tracer, means for feeding the cutter and tracer toward the work and pattern respec tively to effect engagement of the tracer with 'the rotating pattern at some random point in the periphery thereof, a mechanism for progressively measuring the angular rotation of the work and pattern. means responsive to engagement of the tracerwith the pattern at said random point to activate said mechanism, a control element actuable by said mechanism upon completion of a predetermined angle of rotation, and means responsive to actuation of said control element for eifecting disengagement of the cutter and tracer from the work and pattern respectively, whereby the cutter will be eiiective on the work for a predetermined angle of work rotation measured from said random point.

2. In a pattern controlled machinetool having work and pattern supporting means, and power operated means eflfecting continuous rotation of said work and pattern supportingmeans, the combination of a cutter and tracer, means for feeding the cutter and tracer into engagement with the rotating work and pattern respectively whereby the cutter will engage the work to a predetermined depth at some random point circumferentially thereof, means for measuring a predetermined angle of rotation of said work and pattern supporting means, means responsive to engagement of the tracer with the pattern to eii'ectintercoupling of said measuring means with said power operated means whereby said predetermined angle will be measured from said random point of cutter engagement, said measuring means including a control operable thereby and eilective on said feeding means to sheet retraction of the cutter and tracer.

3. In a pattern controlled machine tool having continuously rotating work and pattern supports and a cutter and a tracer for engagement with the work and patternrcspectively carried by said supports, the combination of means for feeding the cutter and tracer into engagement with the work and pattern whereby actual engagement will occur at some random point on the periphery of the work and pattern, measuring means adjustable to measure a predetermined angle of rotation of the work and pattern, means responsiveto engagementof the tracer with the pattern to intercouple said measuring means for actuation in timed relation with the rotating supports whereby said predetermined angle of rotation will be measured from said random point, means rel4 1 spousive to completion of said measurement and eifective on said feeding means to effect retrac tion of the cutter and tracer. means responsive to said retractive movement to effect indexing of the tracer and cutter and subsequent reengagement with the work and pattern whereby the cutter may be immediately, reengaged with the work regardless of its rotary position.

4. In apattern controlled milling machine having work and pattern supporting means. the combination with power operable means continuously rotating said supporting means, and a cutter and tracer movable into and out of engagement with the work and pattern respectively whereby the cutter and tracer will engage the work and ,pattern at some random point in the periphery thereof. of an angular rotation measuring means adjustable for measuring a complete revolution or other than a complete revolution of said supporting means, and means responsive to engagement of the tracer with the pattern to connect said measuring mechanism with said power operable means for actuation concurrently with said work and pattern supporting means whereby said revolution or other than said revolution of said supporting means will be measured from said random point,

5. In a pattern controlled milling machine having rotatable work and pattern supporting means, and means continuously rotating said supporting means, the combination with a cutter and tracer, of means for moving said cutter and tracer into engagement with work and pattern carried by said supporting means whereby said engagement will be effected at some random pointin the periphery of the continuously rotat ing work and pattern, a measuring mechanism adjusted to measure more than a complete revolution of the work and pattern supporting means, meansresponsive to engagement of the tracer with the pattern for coupling said measuring mechanism with said rotating means whereby the angle of revolution of the work supporting means will be measured from said random point so that the cutting path of the cutter will be made to overlap regardlessof the random point tion, electrical means for detecting the random point at which the cutter reached said predetermined depth and simultaneously effecting coupling of the measuringmeans with said work supporting means for concurrent progressive actuation with said worksupporting means, and mechanism including control means operable by said measuring means for automatically effecting retraction, indexing and reengagement of the cutter with the work automatically for machining the next annular surface. 7. In a machine tool having a rotating wor support and a cutter supported for feeding movement into the periphery of the rotating work on said support, the combination of meansfor continuously rotating the work support, means for detecting the random point at which the cutter asaaase rotatable with the work support, means for measuring the angle of rotation of the work support from said random point, hydraulic means operable by said detecting means for coupling said measuring means with said rotor simultaneously with depth engagement of the cutter with the work.

8. In a machine tool having a rotating work support, power operable means for continuously rotating said support, and a cutter feedable to a predetermined depth into cutting engagement with the work, the combination of means for detecting the random point at which the cutter reached depth in the work circumferentially thereof, a measuring mechanism for determining the angle of rotation of the work from said random point, means operable by said detecting means for automatically coupling said measuring means to said power operable means for concomitant angular rotation with the work, said measuring means including a trip operable control device, and means responsive to actuation of said device to effect retraction of the cutter.

9. In a machine tool having a power operable rotating work support, and a cutter feedable to a predetermined depth into the work at a random point circumferentially thereof, the combination of means for determining the length of the cutting path from said random point including a control member, means for automatically coupling said member to the work support for simultaneous angular movement with the work, means for determining the time of engagement of the cutter and effecting 'said automatic coupling, a trip operable member in the path of said control member, means to eifect relative adjustment between said members to effect variation in the timing of operation of said trip operable member, and means operable by said trip operable member to effect disengagement of the cutter from the work.

10. In a machine tool having a power operable work support and a cutter movable into engagement with the moving work at a random point thereof, means for measuring the length of the cutting path after said engagement including a movable control member, a positive stop for said member serving as a reference starting point, means normally maintaining said member in engagement with said stop, a clutching means, means determining the time of engagement of the cutter at said random point and causing engagement of said clutching means to connect said control member for concomitant movement with said work, a trip member operable by said control member, and means responsive to operation of said trip member to effect disengagement of said cfutching means and retraction of the cutter whereby said control member will automatically return to its starting position.

11. In a machine tool having a power operable work support and a cutter movable into engagement at a random point with the work during travel thereof, the combination of measuring mechanism for determining the length of the cutting path subsequent to said engagement including a pair of telescoping members one of which is connected for activation with the work support, means for connecting said members for joint rotation to effect activation of said measuring mechanism including a pressure pocket formed in one side of one of said members, and means to admit pressure to said pocket to effect binding of said members together for joint rotation.

12. In a pattern controlled milling machine having work and pattern supporting means, power operable means for continuously rotating said supporting means and a cutter and tracer movable into and out of engagement with the work and pattern respectively whereby the cutter will engage some random point in the peripher of the work, an angular rotation messuring means for the work supporting means, a clutch for coupling said measuring means with said power operable means, an electrical control circuit for controlling engagement of said clutch including a control switch operable by the tracer upon engagement with the pattern, and means responsive to engagement of said clutch for nullifying said switch.

13. In a pattern controlled milling machine having work and pattern supporting means. power operable means continuously rotating said supporting means, and a cutter and tracer movable into and out of engagement with the work and pattern respectively whereby the cutter will engage a random point on the periphery of the work, the combination of an angular rotation measuring means, means operable by the tracer upon engagement with the pattern for automatically coupling said measuring means for angular rotation by the work supporting means. means operable by the measuring mechanism after a predetermined angular rotation to automatically eflect retraction of the tracer and cutter and simultaneous disengagement of said coupling means, and means responsive to said retraction to effect indexing of the cutter and tracer relative to the work and pattern.

14. In a pattern controlled milling machine, a plurality of rotatable work supports and a. rotatable pattern support, a hydraulic motor continuously rotating said supports in synchronism, a source of fluid pressure, means for connecting said source of fluid pressure to said motor to effect a continuous basic slow speed rotation of said supports, a cross slide, a hydraulic cross slide actuator, a metal working tool carried by the cross slide, a tracer controlled valve including a tracer engageable with a pattern for reversibly connecting fluid pressure to said actuator to control movement of the tool in accordance with the pattern, means in said tracer control valve for amplifying the supply of fluid pressure to said motor to increase the basic rate of rotation of said supports and to vary the rate of rotation in accordance with the pattern, an angular rotation measuring mechanism for said supports, means to set said mechanism for a predetermined angle, clutch means responsive to deflection of the tracer upon engagement with the pattern for coupling said mechanism for rotation with said supports and means responsive to said mechanism upon completion of said angle "of rotation to connect fluid pressure to said cross slide actuator.

15. In a pattern controlled milling machine having rotatable work and pattern supports, a feed drive motor synchronously rotating said supports, a fluid pressure pump connectable to said feed motor to effect a continuous basic rate of rotation of said supports, a cross slide movable to and from said supports, a hydraulic actuator connected to said cross slide, a tracer control valve including a tracer adapted to reversibly connect fluid pressure to said cross slide, means in said tracer control valve rendered onerative upon engagement of the tracer with the pattern to increase and vary the basic rate 0! said feed motor. an angular rotation measuring device. means operated by the initial engagement of the tracer with the pattern to couple said device for rotation with said supports, said device being set for a predetermined angle of rotation, and means responsive to completion of said angle of rotation to connect fluid pressure to eifect withdrawal of the cross slide and further mechanism subsequently operated by said device to cause withdrawal of said cross slide.

16. In a pattern controlled milling machine, a frame, a rotatable work table and a rotatable pattern table journaled on said frame, means continuously rotating said tables in timed relationship. a cutter and tracer carrier, means controlled by a tracer on said carrier to cause relative movement between said carrier and tables to efleet engagement of the tracer with a pattern on said pattern table, an angular rotation measuring mechanism for said tables comprising a sleeve journaled in said frame, a clutch operable in response to engagement of the tracer with the pattern to interconnect said rotating means with said sleeve, a pinion formed on said sleeve cooperating with a rack mounted for sliding movement in said frame, and a control device, operable by the movement of said rack to a predetermined position upon rotation of said pinion to cause withdrawal of said cutter and tracer carrier from said spindles.

17. In a pattern controlled milling machine having a rotatable work and pattern table, a cutter and tracer carrier movable radially to and from said spindles, a measuring device for determining the angle of rotation of said tables from the point of initial engagement of the tracer with the pattern comprising a mechanical operator, means for effecting connection of said operator to one of said tables for movement therewith, and control means operated by said operator after a predetermined movement defining a predetermined amount of angular rotation to automatically cause withdrawal of said cutter and tracer carrier from said table.

18. In a pattern controlled milling machine having a continuously rotating pattern support, the combination therewith of a slide carrying a deflectable tracer, said slide being guided for advance and retractive movements with respect to said pattern supporting means, said tracer being movable between spaced operative positions, the first of which causes advance and the second causes retraction of said slide, control means for positioning the tracer in said first position to connect a source of power for causing advance of the cross slide and engagement of the tracer with the pattern, and means for measuring the extent that the tracer will scan the pattern after engagement therewith includ-- ing an angular rotation measuring device, means responsive to movement of the tracer upon engagement with the pattern to eflect interconnection of said device for joint rotation with the pattern support, means to set a limit on the angle of rotation of said device, and means responsive to said device upon reaching the limit of its rotation to effect positioning of the tracer in its second position to cause disengagement of the tracer with the pattern.

JOHN Q. Booms,

GEORGE A. LENSKY.

wm'rnaor TRIBLE.

REFERENCES CITED The following references are of record in the file of this patent:

.UNI'I'ED STATES PATENTS 

